Turbine



3 Sheeilzs-Sheet l A. s. MILLER TURBINE Filed Nov. 8, 1955 d M., \\mw..nM. V R w NNW M, N lx1 Y xm N N Y l m \I k QN NN fmw .WWI WMV I|IMWMJV LAv k M. .Q

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Nov. 12, 1935.

A. S. MILLER Nov; 12, 1935.

' TURBIN F'iled NOV. 8, 1955 3 Sheets-Sheet 2 NhOV. 12, 1935. i Al 5MlLLER '2,021,078

TURBINE Filed Nov. 8, 1955 3 sheets-sheet 5 Patented Nov. 12, 1935UNITED STATES @ATENT OFFICE 9 Claims.

This invention relates to turbines and, more particularly, to turbinesfor general use. Heretofore, existing turbines have been too heavy andexpensive for general use and their range of use-- fulness has,accordingly, been limited. The general object of the present inventionis to provide an improved turbine or like engine which, by virtue ofcertain novel features of construction, lobviates the objectionablecharacteristics of prior devices of this class and lends itself toefficient and economic general use.

A more specific object of the invention is to provide a radial flowmulti-stage turbine of the impulse and reaction type having aself-balanced rotoriand in which vibration and axial thrust issubstantially eliminated. The construction of the device is such thatthe maximum pressure of the steam or other impelling medium is con--fined within the rotor unit, the interior wall of the housing of thedevice not being subjected to such maximum pressure.

Other objects and features of the invention will appear hereinafter. Theinvention may be clearly understood from the following detaileddescription of the exemplary form illustrated on the drawings.

In the drawings:

Fig. 1 is an elevational view of the device showing a substantialportion of the same in section;

Fig. 2 is a sectional View taken along line 2 2 of Fig. 1;

Fig. 3 is a sectional view taken along line 3-3 of Fig. 1;

Fig. 4 is a detail sectional view of one of the end bonnets of thedevice;

Fig. 5 is a detail View illustrating clearly the construction andarrangement of the rotor and stator vanes or blades;

Fig. 6 is a perspective view of one of the vanes;

Fig. 7 is a perspective view of the spacing block or tting piece whichis used to secure the vanes in place; and Fig. 8 is a face View of oneof the housing heads with the bonnet removed, a portion being shown insection.

Referring to the drawings and particularly to Fig. l, the vdevicecomprises generally a stator assembly I and a rotor assembly 2. Thestator comprises essentially a housing 3 which is preferably formed ofhalf cylindrical section I and 5 bolted together as at 6. Section 4constitutes the base of the housing and it is formed to provide a pairof axially spaced exhaust chambers 1 located symmetrically With respectto the center of the device. The exhaust chambers communicate withexhaust ports 8. The steam or other impelling medium enters the exhaustchambers directly from the rotor stages so that the exhaust steam `isevacuated freely without 5 obstructing the passage of exhaust steamleaving the rotor chamber which would lower the eiliciency of theturbine. The location of the ex-n haust ports in the lowest part of thehousing also prevents moisture from collecting in the 10 rotor chamber.The exhaust pipes may be connected as illustrated in Fig. 3 or in anyother suitable manner. Y

Section i of the housing is alsoformed to provide an admission channel 9which is central- 15 ly located between the exhaust chambers and whichmay be arranged for a pipe connection as illustrated in Fig. 2. Byhaving the admission or inlet channel, as well as the exhaust chambers,in the lower part of the turbine so that connections are made to thelower part, the construction of the device is simplified and disassemblyfor repair or replacement of the parts is greatly facilitated. Thisfeature, in conjunction with the two-part construction of the housing,enables the ready removal of the upper seotion 5 which gives access tosubstantially the entire interior of the device and particularly to therotor assembly thereof. In addition, the feature in question enhancesthe balancing of the device due to the manner of admission of the steam,or other impelling medium, and its equal and uniform `distribution tothe axially divided halves thereof and to the rotor stages of each half.

A pair of circular removable heads I0 form part of the stator assemblyand serve to close the ends of the housing. These heads have theircircumferential portions rigidly secured in annular channels II formedon the inside wall at each end of the housing. An opening is pro-- videdthrough the center" of each head to admit the rotor shaft I2. On theouter side of each head and centrally located with respect thereto is acircular recess I3 formed by the annular 45 projection M, into whichrecess a bonnet I5 is fitted, the bonnet being bolted to the head as ati6. Inside each bonnet is a bearing I'I for the rotor shaft which isthus rigidly supported and accurately aligned with respect to thehousing.

As shown in Fig. 4, the bearing supporting sleeve portion of each bonnethas its interior surface formed to provide grooves or recesses I8 whichprovide a tortuous path for the flow of lubricant. It will be seen thatintercommunicating longitudinal and arcuate grooves are provided. Eachbearing is perforated throughout its yentire circumferential surface, asat E8', the openings being tapered inward, as illustrated. A continuousflow of lubricant, which cools the bearing as well as lubricates therotor shaft journals, may be had by providing pipe connections tobonnets, as illustrated. The lubricant flows throught the tortuous pathof the bonnet and is distributed through the bearing openings to thebearing and shaft surfaces. Each bonnet may be provided with a drainopening I9.

Arranged on the rotor shaft is a collar 2B which is mounted upon theshaft so as to revolve therewith and abuts against the bearing,preventing axial or longitudinal movement of the rotor shaft and therotor assembly carried thereby. Collar 2i! has a sleeve portion 2l and aflange 22. A slidable collar 23 is mounted on the sleeve portion ofcollar 20 so as to revolve therewith. There are provided a plurality ofcoiled springs 24 which are `arranged to urge collar 22 away from ange2l and into light engagement with .a hollow ring 25 which surroundssleeve portion 2| and is secured to head l. An annular recess or channel263 is provided in collar 23 and is adapted to receive Vpacking toprevent leakage of oil or other lubricant into the rotor chamber fromthe bearing. The hollow ring 25 has circulating therethrough a coolingfluid which serves to reduce the temperatureeinside bonnet l5 andinsures a cool bearing. The inner side of ring 25 is preferablyinsulated to prevent the transfer of heat between the bearing and therotor assembly. As shown more clearly in ,Fig.v8,'pip-es 21 extendthrough openings in head IU to ring 25 in order that a continuous ow ofcooling fluid may be had through ring 25. The specific arrangement ofthe collars effectively prevents leakage of the lubricant between thebearing compartment and the rotor chamber, while ring 25 effectivelycools the bearing and prevents heat transfer. a

Coming now to the rotor assembly, there is keyed on the rotor shaft oneach side of the center of 'the device a plurality of rotor disks orwheels 2B and 29. These diskshavetheir hubs in abutment as shown. VThedisks 28 are substantially similar to each other and constitute theinner disks, while disks 29 are differently constructed and constitutethe outer or end disks. Each of the disks 23 is provided with aplurality of circularly arranged openings 3B immediately adjacent itshub, the purpose of these openings being to transmit steam, or otherimpelling medium,centrally and axially of the device from the centertowards the ends thereof. Each of the rotor disks is tapered outwardlyso as to have a diminishingarea of cross-section from the hub to theperiphery. On their faces, the rotorl disks are provided with concentricbeveled or dovetailed grooves 3l at regular Vintervals from a point nearthe shaft to a point adjacent the periphery of the disks. Firmly securedin the grooves are the rotor blades or Avanes 32 see Fig. 6) whichproject at right angles to the vfaces of the disks vand have theircurvedsides inclined in a direction parallel to the line of rotation4 ofthe disks, as

illustrated more clearly in Figs. 2, 3 and 5.

Arranged alternately between the rotor disks are the stator disks orwheels 33 and 34. Disks Zi are shaped generally similar to the rotordisks each having a radially diminishing area of crosssection. Thesedisks have their circumferential portions securediin annular recesses orchannels form-ed on the inner wall of the housing. A

large circular passage is provided in the center of these stationarydisks'to admit the rotor shaft and the hubs of the `rotor wheels and toserve as a steam passage to adjacent rotor stages.V On

their faces, these disks are provided with grooves 5 36 .and vanes 37,which are similar to the corre-` sponding elements of the rotor disks,but vanes 3l are inclined in a direction opposite that of the rotorvanes 32, as illustrated clearly in Figs. 2, 3 and 5. Each row of statorvanes is-positioned 10 directly between adjacent rows of the rotor vanesso that the rotor and stator vanes intermesh, as

' clearly illustrated in Fig. 1.

The'centrally located stator disk 34 is of different construction thanthe other stator disks and 15 is formed to provide an admission port 38leading from the admission channel 9 radially to the centrally locatedannular chamber 39. Aside from its peculiar construction to provide foradmission of the steam, or other impelling medium, this disk 2() isgenerally similar to the other stator disks and is similarly secured inan annular recess or channel 40 formed in the inner Wall of the housing.The details of construction of this disk, particularly as regards theadmission port, are shown 2.5 clearly in Figs. 1 and 2. The disk isprovided on its periphery with a projection 4| through which theadmission port extends and the projection is seated in a recess 42 inthe lower part of the housing where the admission port communicates 30with admission channel 9.

curved radially, as illustrated in Fig. 1, to cor` 35 respond with theinner face of the housing to which it is in close proximity. These rotordisks have no steam passages through their central parts `and steam, orother impelling medium, cannot pass axially beyond them. It must, there-40 fore, take its course through the vanes on the inner side of thesedisks. InV consequence, live steam under pressure does not contact withthe inner wall of the housing and the housing wall is, therefore, notsubjected to maximum steam 5 pressure. This arrangement makes a heavyhousing unnecessary even though superheated, high pressure steam may beemployed. Furthermore, the heat absorbed by the heads of the housing ismuch reduced `due to the avoidance of contact 50 with live steam andthis aids in the cooling of the bearing compartment. l

Referring particularly to Fig. 5 of the drawings, there Vis shown incross-sectio-n a row or series of rotor vanes A and an adjacent row or5`5` seriesrof stator vanes B in cooperative relation with the rotorvanes. The opposite inclination of the two sets of vanes ,is clearlyshown. The vanes are identical in shape and area of crosssection andtheir sides converge into points at llt and 45. A portion of the outeror convex side of the vanes at 45 is arranged substantially parallel tothe circular line or plane withinY which they are located. Both sets ofvanes are arranged in each of their respective circles so as to providea wide inlet at 46 and a relatively narrow outlet at 4l. It will benoted from Eig. Yl that the length of the vanes increases in proportionto their distance from the rotor shaft and the area of the passagesbetween them increases in a corresponding vmanner due to the gradualreductions radially in cross-sectional area of the stator and rotorwheels. This permits the gradual increase in volumeof the steam toexpand to a desired range of pressure with a minimum of friction in itspassage through the turbine.

Also, in consequence of the uniform setting oi all the vanes in therotor unit, there is an increasing number of vanes in each series fromthe shaft outward. The resultant increase in the number of passagespermits the gradual increase in the volume of the steam to expand to adesired range of pressure in each series of vanes. The increasing volumeof the steam is by the described arrangement automatically taken careof. As the volume of the steam increases in each series of vanes, thepressure decreases and the velocity of the steam increases in acorresponding manner.

The vanes may be fastened in the grooves of the rotor and stator disksin any suitable manner. For example, the vanes may be formed asillustrated in Fig. 6 and may be secured in the grooves by spacingblocks made of soft tough metal, such as that shown in Fig. '7. It willbe seen that the vanes are provided with beveled portions d8corresponding to the sides of the beveled or dovetailed grooves, whichbeveled portions are adapted to seat snugly in the said grooves. Thevanes, when thus formed, may be individually positioned in the groovesby inserting each vane lengthwise in the groove and then turning thevane until it is inclined at the proper angle with the beveled portions68 seated in the sides of the groove. One side of the spacing block iscurved to conform with the convex side of the vane, While the other sideof the block is curved to conform with the concave side of the vane. Theblock is of a thickness slightly greater than the depth of the groove.After each vane is inserted in the groove in the manner above described,a spacing block may be placed in the groove in the same manner, that is,the block may be inserted lengthwise in the groove and then turned tocause its beveled sides to seat in the sides of the groove. The vanesand spacing blocks are thus inserted and secured alternately in a grooveuntil the groove is completely filled.

It will be observed that the last spacing block to be inserted in thegroove between the first and last vanes cannot be placed in the groovein the manner described. rIhis block may be bent so that it may bepositioned in the groove without turning and the block may then bestraightcned out so that its beveled ends will seat themselves againstthe beveled sides of the groove. The vanes and blocks are so designedthat they completely fill the groove and the vanes are equally spaced.Although the vanes will be rigidly secured in the groove, when assembledwith the spacing blocks as above described, the blocks may be upsetafter all the vanes in a circle are placed in position to further insurethe security of the vanes. Tests have shown that the vanes are socompletely anchored in the groove when assembled as described that it isimpossible to dislodge them without mutilating them. This solid settingof the vanes is not aiected by expansion or contraction due to varyingtemperatures. The space between the vanes is smooth and flush with theface of the wheel or disk, oifering no obstruction to the steam in itspassage.

In operation of the device, steam or other impelling medium, at maximumpressure enters the admission chamber 9 and passes radially through port38 to the annular chamber 39 from which it passes axially in bothdirections through the openings of the rotor disks and the annularspaces therebetween. The steam is thus distributed equally and uniformlyto both sides of the turbine and it is then distributed uniformly to therespective rotor stages of each section. As it passes simultaneouslythrough the various rotor stages, the steam is guided by the statorvanes 5 so as to strike the rotor vanes on the inner side of theircurved portion at M with great force.

The jets of steam are not distorted by the impact but follow the curvedpath i4-45 of their passages. As the steam expands in the passages 10formed by the vanes, the resultant back pressure would be taken on thepoint 45 of the stator vanes but the pressure and velocity of the jetsof steam continuously entering the passages of the rotor vanes act as abarrier across the inlet 46 of the 15f rotor vanes which tends to forcethe expanding steam into the passages. This action of the steam resultsin an even pressure being maintained in the passages and the velocity ofthe steam as it leaves the passages continues to in- 20,r

crease in correspondence With the increase in volume. This action of thesteam is repeated in each series of vanes until the point of exhaust isreached.

A minute fraction of clearance is provided be- 25 tween each series ofstationary and moving vanes and between outer ends of the vanes andadjacent faces of rotor members. As a result, leakage and entrainment ofsteam between each series of vanes is reduced to a minimum. 30

The stabilizing effect produced on the rotor wheels by the tensioneffective radially against points 4d and Q5 of the running vanes fromthe expanding steam entering and leaving the passages in each series ofvanes tends to reduce the 35 .centrifugal force induced by the speed onthe rotor wheels. The constant tension in opposite directions bothradially and axially, exerted by the steam on each rotor wheel, resultsin a perfect balancing of the rotor and a complete ab- 4Q sense of rotorvibrations.

Since these conditions are obtainable in a high speed turbine, greatereconomy in steam consumption can also be accomplished. In a turbine asdescribed and shown on the drawings, the 45 uniform arrangements of thevanes, their 'curvature, pitch of inclination and area of port opening,preclude any waste or dissipation of the steam which, when entering theturbine, applies its expansive force most effectively against the 50Hrunning vanes. The energy expended in the process of turning the rotorwheels develops a power which is proportionate to the speed of therotor. That speed, and the volume of steam passing through the rotorunder a given pressure is v largely determined by the describedarrangements of the vanes. A high speed steam turbine of the typedisclosed herein is very desirable, as satisfactory speed-reducingappliances are now employed in connection with high speed engines andmotors which make a high speed steam turbine practicable.

Although there is illustrated and described herein a single preferredembodiment of the invention, it will be understood that this is forpurposes of illustration only and does not limit the scope of theinvention. Any changes or modifications which fall within the scope ofthe appended claims are deemed to be Within the spirit and scope of theinvention.

I claim:

l. In a turbine, a housing formed to provide a pair of axially andsymmetrically spaced exhaust chambers and ports and a centrally disposedadmission channel in its base, a central stationary disk within saidhousing having an admission port leading from said channel to an innerannular chamber, and a rotor comprising a rotatable axial shaft, and aplurality of vane-carrying disks mounted o-n said shaft and disposedsymmetri- 'cally with respect tosaid central stationary disk, each saidrotor disks having a plurality of circularly arranged openingstherethrough adjacent said shaft and in communication with said annularchamber, wherebyY steam or other impelling medium is admitted centrallyof the device and is passed axially of the device and supplied to all ofthe rotor stages simultaneously through whichit flows radially outwardto said exhaust chambers.

carrying disks mounted on said shaft and dis" .posed alternately withrespect to said stationary disks and symmetrically with respect to saidcentral stationary disk, each said rotor disks having a plurality ofcircularly arranged openings therethrough adjacent said shaft and insubstantially axial alignment with 4the stator disk openings and saidannular chamber, whereby steam or other impelling medium is` admittedcentrally of the device and is passed axially of the device and suppliedto all of the rotor stages simultaneouslyV through which it flowsradially outward to. said exhaust chambers.

3. In a turbine, a housing formed to provide a pair of axially andsymmetrically spaced exhaust chambers and a centrallyV disposedadmission channel in its base, a central stationary vane-carrying diskwithin said housing having an admission port leading from said channelto an inner annular chamber, a plurality oi spaced stationaryvane-carrying disks disposed symmetrically with respect to said centralstationary disk and each having a central opening, and a rotorcomprising a rotatable axial shaft, and a plurality of Vanecarryingdisks mounted on said shaft and disposed alternately with respect tosaid stationary disks and symmetrically with respect to said centralstationary disk, each said rotor disks having a plurality of circularlyarranged openings therethrough adjacent said shaft and in substantiallyaxial alignment with stator` disk openings and said annular chamber,whereby steam or other impelling medium is admitted centrally of thedevice and is passed axially of the device and supplied to all of therotor stages simultaneously through which it ilows radially outward tosaid exhaust chambers, the rotor and stator vanes intermeshing with eachother and being inclined in opposite directions.

4.V In a turbine, a housing formed to provide a pair of axially andsymmetrically spaced exhaust chambers and ports anda centrally disposedadmission channel in its base, a central stationary 'vane-carrying diskwithin said housing having an admission port leading from said channelto an inner annular chamber, a plurality of spaced stationaryvane-carrying disks disposed symmetrically with respect to said centralstationary disk and each having a central opening, and a rotorcomprising a rotatable axial shaft, and a plurality ofvane-carryingdisks mounted on said shaft and disposed alternately withrespect to said stationary disks and symmetrically with respect to saidcentral stationary disk, each said rotor disks having a plurality ofcircularly arranged openings therethrough adjacent said shaft and in Ysubstantially axial alignment with the stator disk openings and saidannular chamber, whereby steam or other impelling medium is admittedcentrally of thedevice and is passed axially of the device and suppliedto all of the rotor stages simultaneously through which it ows radiallyoutward to said exhaust chambers, the rotor and stator vanesintermeshing with each other and increasing in length proportionately totheir distance from the axis of the device and being inclined inopposite directions.

5. In a multi-stage turbine, means for admitting an impelling mediumcentrally of the turbine, a rotor comprising a rotatable axial shaft anda plurality of vane-carrying disks mounted on said shaft, said rotordisks having openings therethrough adjacent said shaft, whereby theimpelling medium is passed axially of the turbine in opposite directionsand is supplied to al1 of the rotor stages simultaneously through whichit flows radially outward, and means for exhausting the impelling mediumafter it has passed through said stages.

6. Ina multi-stage turbine, means for admitting an impelling mediumcentrally of the turbine, a rotor comprising a rotatable axial shaft lnately with respect to said rotor disks `and each ting an impellingmedium centrally of the turbine, a rotor comprising a rotatable axialshaft and a plurality of outwardly tapered vane-carrying disks mountedon said shaft, said rotor disks having openings therethrough adjacentsaid shaft, a plurality of stationary outwardly tapered vane-carryingdisks disposed alternately with respect to said rotor disks and eachVhaving a central opening in substantially axial alignment with therotor openings, whereby the impelling medium is passedv axially of theturbine in opposite directions and is supplied to all of the rotorstages simultaneously through which it iiows radially outward, and meansfor exhausting the impelling medium after it has passed through saidstages.`

8. In a multi-stage turbine, means for admitting an impelling mediumcentrally of the turbine, a rotor comprising a rotatable axial shaft anda plurality of outwardly tapered vane-carrying disks mounted on saidshaft, said rotor disks having axially-extending abutting hubs andopenings adjacent said hubs, a pluralityof stationary outwardly taperedvane-carrying disks disposed alternately with respect to said rotordisks "and each having a central opening in substantially axialalignment with the rotor open- Y ings, whereby the impelling medium ispassed axially of the turbine in opposite directions and is supplied toall of the rotor stages simultaneously through which it flows radiallyoutward, and means for exhausting the impelling medium after it haspassed through said stages.

9. 1n a multi-stage turbine, means for admitting an impelling mediumaxially of the turbine, a rotor comprising a rotatable axial shaft and aplurality of vane-carrying disks mounted on said shaft, said rotor diskshaving openings therethrough adjacent said shaft, a plurality ofstationary vane-carrying disks disposed alternately with respect to saidrotor ydisks and each having a central opening in substantially axialalignment With the rotor openings, whereby the impelling medium ispassed axially of the turbine and is supplied to all of the rotor stagessimultaneously through Which it ilows radially outward, and means forexhausting the impelling medium after it has passed through said stages.

ANDREW S. MILLER.

